CN103459798A

CN103459798A - Controllable cooling system for a motor vehicle, coolant pump therefor, impeller for use in the coolant pump, and method for controlling a coolant flow in such a cooling system

Info

Publication number: CN103459798A
Application number: CN2011800689663A
Authority: CN
Inventors: 弗朗茨·帕韦莱克
Original assignee: Geraete und Pumpenbau GmbH
Current assignee: Nidec GPM GmbH
Priority date: 2011-03-04
Filing date: 2011-11-29
Publication date: 2013-12-18
Anticipated expiration: 2031-11-29
Also published as: US20130333863A1; WO2012119622A2; CN103459798B; DE102011001090A1; ES2587598T3; WO2012119622A3; EP2681425B1; EP2681425A2

Abstract

The invention relates to a controllable cooling system (1) for a motor vehicle comprising a coolant circuit, which delivers a coolant to an internal combustion engine and draws off coolant therefrom, as well as a mechanically operated controllable main coolant pump (3) and an electrically operated controllable secondary coolant pump (5). The cooling system further comprises a control device which controls the main coolant pump (3) and the secondary coolant pump (5) on the basis of operating states of the internal combustion engine. The invention further provides an electrically operated controllable secondary coolant pump (5) for such a cooling system (1), an impeller (25) which can be used in said secondary coolant pump (5) and a method for controlling the coolant flow in a such cooling system (1).

Description

For the controlled cooling system of motor vehicle, for the coolant pump of cooling system, impeller that coolant pump uses and control the method for the cooling liquid stream of described cooling system

Technical field

The present invention relates to a kind of controllable cooling system for motor vehicle according to claim 1, a kind of power-actuated controllable coolant pump according to claim 6 that is applicable to described system, a kind of according to the impeller in the described coolant pump of being used in of claim 22 and a kind of method for the coolant rate of controlling described cooling system according to claim 30.

Background technique

Mechanically operated coolant pump is applied in motor vehicle usually, so that the cooling liquid in coolant circuit circulates between vehicle radiator and internal-combustion engine.This coolant pump is designed to axial-flow pump or radial flow pump, and described coolant pump is disposed between described vehicle radiator and internal-combustion engine.

Described coolant pump is driven by the driving force of internal-combustion engine via belt transmission.The example of this pump was carried out discussion in same application DE102005004315B4 and DE102005062200B3.

Due to the shortage day by day of mineral fuel, it is oil-saving efficient and the vehicle of saving the energy that current automotive department divides the focus of development.Startup-halt system is used to internal-combustion engine in Temporarily Closed vehicle for example (for example when at red light or the parking when the railway sluice gate etc.).For example finish traffic lights once the situation of stopping and turn green and vehicle driver and drive gas pedal, described internal-combustion engine restarts.

Yet, due to closing of the internal-combustion engine system inherence in the described startup-halt system in the modern automotive vehicle, described coolant pump also can be out of service.Specifically, because the shutdown of internal-combustion engine no longer includes driving force and is delivered to described coolant pump via belt transmission, this causes that the out of service and described cooling liquid of described coolant pump no longer circulates in described cooling circuit.

When especially externally higher the or motor of temperature and/or coolant temperature are higher, this may raise the temperature to and surpass the rank allowed.

So the situation that the cooling liquid when internal-combustion engine quits work in cooling circuit continues to circulate in having the vehicle of startup-halt system can substitute common adopted mechanically operated pump with power-actuated coolant pump on principle.

Yet electric coolant pump demonstrates following shortcoming: they are must size enough large to produce enough cooling capacities.So this large-sized power-actuated coolant pump must fully be driven by vehicle-mounted automotive power.

Because this may must compensate via the alternator of automobile, therefore described alternator must produce more energy Vehicular accumulator cell is remained on minimum battery charge level and to described vehicle-mounted power and carries out sufficient Power supply, using motor-drive pump as the coolant pump for motor vehicle, uses and does not also become so far very extensive.

However, for the possibility of coolant rate that the abundance of guaranteeing modern startup-halt system is provided, attempted recently providing a kind of coolant pump of the transformation that electric drive and Mechanical Driven are combined.

An example of this coolant pump is designed to the mixed power coolant pump, and it is upper that it is disclosed in periodical MTZ, number of the edition 11,2010(journal MTZ, issue11,2010).The mixed power coolant pump that discuss in this place is by the drive force of the internal-combustion engine of the main driving of conduct via with transmission.This pump also comprises a kind of brushless electric machine in its housing; described brushless electric machine is connected to live axle via clutch; and strengthen the described driving force with transmission, or the liquid circulation of only when described engine shutdown, taking over described startup-halt system.

Yet, being disclosed in periodical MTZ, the mixed power coolant pump in number of the edition 11,2010 is unsuitable for all internal combustion engine operation operating modes are made to gratifying response.

Specifically, periodical MTZ, the mixed power coolant pump of discussing in number of the edition 11,2010 can not guarantee by the described coolant rate of the interruption of not revealing the rapidly pre-warming circulation of internal-combustion engine.Then speech, can not there is so-called impounded water with this open type coolant pump.In fact on the liquid circulation on a specific basis, always can be observed, and the preheating operation therefore accelerated can not be implemented.

In fact, periodical MTZ, the article about the mixed power coolant pump in number of the edition 11,2010 has discussed, and such pump can be motorless therefore to carry out the preheating program of the acceleration in internal-combustion engine.

But the mixed power coolant pump of design can not be avoided backflow or the leakage of the cooling liquid of described pump like this, this may cause that circulating load is extremely low and therefore postpone preheating program.

In addition, can not use periodical MTZ, number of the edition 11, in 2010, disclosed pump according to different internal combustion engine operation operating modes (for example comes, idle mode, overrun mode or other possible pattern) suitable liquid circulation flow rate is set respectively, and suitable liquid circulation flow rate can allow described coolant temperature to be maintained in a temperature range desirable for corresponding operating conditions.

Therefore periodical MTZ, in number of the edition 11,2010, disclosed pump also demonstrates following shortcoming: when described pump during via belt wheel and via internal combustion engine operation, the motor that is arranged in described pump case serves as generator.Therefore must produce the electric energy corresponding with export and supply with described vehicle-mounted power system from described pump.For fear of described motor-drive pump, as generator, when described motor-drive pump does not need to move, described motor-drive pump must not break away from described axle.

The structure of this mixed power pump proposed is very complicated, and the cost that system increases has surpassed economically viable level.With system commonly used, compare, the efficiency that such pump can be obtained is also relatively low.

Summary of the invention

From the shortcoming of described prior art before, target of the present invention is to propose a kind of cooling system simple in structure, and even when internal-combustion engine is unpowered, described cooling system also can guarantee that cooling liquid constantly enters the cooling circuit of described internal-combustion engine in a steady stream easily.The present invention can further propose a kind of cooling system, relies on described cooling system just can obtain different cooling effects according to the different operating conditionss of described internal-combustion engine.

Can reach this purpose by the cooling system according to claim 1.

According to the present invention, a kind of controllable cooling system for motor vehicle has been proposed, described cooling system comprises cooling circuit, described cooling circuit is for being supplied to cooling liquid the internal-combustion engine of vehicle and cooling liquid is discharged from the internal-combustion engine of vehicle.Be furnished with mechanically operated controllable main refrigerant fluid pump and power-actuated controllable the second coolant pump in described cooling system; Described main refrigerant fluid pump includes an inlet and an outlet, and described entrance is for described cooling liquid is supplied to described main refrigerant fluid pump, and described outlet is for being discharged to described internal-combustion engine by described cooling liquid; Described the second coolant pump includes an inlet and an outlet, and described entrance is for described cooling liquid is supplied to described the second coolant pump, and described outlet is discharged towards described main refrigerant fluid pump for the cooling liquid that will carry as bypass cooling liquid stream; Wherein said the second coolant pump is disposed in the upstream end of the streamwise of described main refrigerant fluid pump, along the direction of coolant flow from the cooling line branch of leading to described main refrigerant fluid, draws.The cooling liquid of utilizing described the second coolant pump to carry is fed into the outlet of leading to described internal-combustion engine with the downstream through described main refrigerant fluid pump and the mode of the described main refrigerant fluid pump of not flowing through.Described the second coolant pump further comprises pump case, in described pump case, is formed with pump chamber, and wherein motor is disposed on the part of described pump case, and described motor relies on the live axle extended in described pump chamber to provide driving force for described the second coolant pump.The impeller that serves as the conveyer assembly is arranged in the pump chamber of described the second coolant pump and is arranged to and described live axle is coaxial and drivable being connected on described live axle, wherein said the second coolant pump comprises the control guiding valve be formed on described impeller, described control guiding valve at least can be moved to " opening " position and " cutting out " position, with for controlling the bypass cooling liquid stream of being carried by described the second coolant pump, be particularly useful for stoping the direction that described cooling liquid is contrary along the throughput direction with described the second coolant pump to reflux.

Can obtain following advantage by cooling system according to the present invention.

Parallel using method using mechanical pump as the main refrigerant fluid pump and using motor-drive pump as the second coolant pump allows to propose a kind of very simple and cheap cooling system, and the characteristics of described cooling system are: simple in structure and even when internal-combustion engine is unpowered and so also can guarantee easily that cooling liquid constantly enters the cooling circuit of described internal-combustion engine in a steady stream can not produce the required driving force of described mechanically operated main refrigerant fluid pump the time.

Here, proved that it is useful retaining described mechanically operated coolant pump in reality in described cooling system, and this allows the efficiency that obtains higher level when moving by described mechanical pump when also selectivity is supported described cooling system by described motor-drive pump.The level of efficiency that can reach according to cooling system of the present invention is far above the situation of above-mentioned single shaft mixed power pump.

In addition, advantageously, comprise that according to of the present invention the cooling system of the pump of two described controls has so-called impounded water, described impounded water can make described internal-combustion engine rapidly pre-warming (especially when cold start-up), so vehicle in a short period of time just can be with optimum temperature/oil consumption operation.

Advantageously, can by control guiding valve (being " to close " position by described guiding valve is moved to it on concrete) in described the second coolant pump guarantee any cooling liquid refluxed from described internal-combustion engine (described backflow due to lack pumping action or pumping action lost efficacy cause) along the direction contrary with the throughput direction of described the second coolant pump, flow towards the radiator of described vehicle.

In addition; also can realize cooling system by controllable power-actuated second coolant pump of the mechanically operated controllable main refrigerant fluid pump with known and the parallel layout of adding; for example, guarantee reliable cooling performance in described cooling system can be in the various situations of the fuel-efficient motor in modern times (startup-halt system, sliding mode under engine shutdown or other situation) automatically, and the cost of development and application is remained in rational scope simultaneously.

In addition, it is before described at periodical MTZ that described global design mechanically operated and power-actuated coolant pump makes them to look like, number of the edition 11, in 2010, disclosed mixed power pump is such, needn't take new bearing and sealing system for water pump spindle, that scheme is suitable for moving chronically continuously and economical and efficient, and what after several years, will become is apparent.

On the contrary, according to cooling system of the present invention, bearing and the sealing system that proves in many ways in practice its value can be adopted, and the reliability of described cooling system and economic operation can be guaranteed.

According to the other embodiment of cooling system of the present invention, it is the theme of dependent claims.

According to an embodiment, described main refrigerant fluid pump comprises pump case, in described pump case, is formed with pump chamber, and the impeller that wherein serves as the conveyer assembly is arranged in described pump chamber and via the drive shaft extended in described pump chamber, preferably, described live axle is driven by the band transmission.

According to an embodiment, therefore described main refrigerant fluid pump can be designed to axial-flow pump or radial flow pump.

In fact, advantageously, described main refrigerant fluid pump is via the band wheel drive on the belt wheel that is connected to described internal-combustion engine, and this makes can be in the situation that drive described main refrigerant fluid pump without any additional driver element.In addition, the oil-engine driven band transmission of use in running makes does not almost have frictional loss, and therefore described main refrigerant fluid pump can move efficiently.

In addition, use utilizes the band transmission of the driving force of described internal-combustion engine to have the following advantages: even when the rotating speed of described internal-combustion engine is very low, still allow to produce rotatablely moving of impeller in described main refrigerant fluid pump, therefore guaranteed the circulation (even in slow-revving situation) of cooling liquid thus avoid reliably motor overheating.

According to another embodiment, described main refrigerant fluid pump further comprises the control guiding valve, described control guiding valve be formed on described impeller and and the coaxial layout of described impeller; Described control guiding valve can at least be moved to " opening " position and " cutting out " position, preferably along described impeller, is arranged in described pump chamber, to control the cooling liquid stream of being carried by described main refrigerant fluid pump.

Advantageously, rely on the control guiding valve of arrangement according to the invention in the main refrigerant fluid pump carry out interruption coolant flow intentionally and therefore do not interrupt the operation of described main refrigerant fluid pump.This that is to say likely under this method, for example, in order to obtain the impounded water of the described internal-combustion engine in cold start-up, guiding valve is moved to it and " close " position, at the described guiding valve closed impeller in described " closing " position and stop the further transfer of the cooling liquid of discharging from discharge point, therefore interrupt the cooling liquid stream of being carried by impeller.

In addition, and the coaxially arranged described guiding valve of described impeller simplified the overall structure of described main refrigerant fluid pump.In other words, needn't use freewheel (freewheel) or analog to interrupt the driving force transmission of the live axle from described internal-combustion engine to described main refrigerant fluid pump.Replace ground, can utilize and move described control guiding valve along the live axle of described main refrigerant fluid pump and interrupt by the liquid circulation of described main refrigerant fluid pump, and can therefore not stop the driving force transmission of the live axle from described internal-combustion engine to described main refrigerant fluid pump.

According to an embodiment, the motor of the second coolant pump is configured to dry type rotor or wet type rotor.

By the motor that is designed to the dry type rotor, for the advantage of described the second coolant pump, be: can make described the second coolant pump there is high rotating speed and small size.

Alternately, the motor that is designed to the dry type rotor is guaranteed to the cooling relatively simple of described motor for described the second coolant pump, because the cooling liquid be present in the vehicle cooling circuit under any circumstance can be used by it.

Use the advantage of this motor to be: to make it possible to that described the second coolant pump is designed to described standard motor-drive pump of standard motor-drive pump while and there is less size, allow with lower original a large amount of manufacture that manufactured.

According to another embodiment, described cooling system further comprises control gear, and described control gear is controlled described the first main refrigerant fluid pump and/or the second coolant pump according to the operating conditions distributed of described internal-combustion engine.

The described control gear proposed according to the present invention is implemented as the software module in control unit for vehicle for example or is designed to a control unit independently; Preferably, make its can control mutually parallel or independently described main refrigerant fluid pump and/or described the second coolant pump to produce all the time required coolant rate in described cooling circuit.

Described control gear especially can be controlled described main refrigerant fluid pump and/or described the second coolant pump so that they and be throttled into and do not have cooling liquid to be recycled during the preheating operation of described internal-combustion engine cold start-up.Described internal-combustion engine one reaches its running temperature, thereby just by movement, be arranged in control guiding valve in pump chamber separately, described two pumps is controlled as being parallel to each other or separating and is controlled described cooling liquid and flow.

Preferably, can be by means of this control and by carry out the temperature of the described cooling liquid of control initiatively with the concrete operating conditions according to described internal-combustion engine with map; For example, when unloaded or when for example vehicle travels in city, make described chilling temperature can be maintained on a level that makes the fuel availability optimum, and therefore can realize the operation of the economical and efficient of vehicle.

The present invention has proposed a kind of power-actuated coolant pump that is applicable to described cooling system on the other hand.

That discusses hereinafter also can obtain and the similar advantage of above-mentioned cooling system according to electric coolant pump of the present invention, so these advantages will not enumerated again.

A kind of power-actuated according to an embodiment of the invention coolant pump, the described power-actuated coolant pump that is particularly useful for above-mentioned cooling system is designed to axial-flow pump or radial flow pump.Described power-actuated coolant pump comprises: pump case; Be preferably flanged entrance and be preferably flanged outlet; Be formed on pump chamber and guiding valve in described pump case, wherein pump impeller is disposed on the pump shaft in described pump chamber, and described pump impeller can be driven by motor by middle pump shaft; Described guiding valve at least can be moved to " opening " and " cutting out " position to control the bypass cooling liquid stream of being carried by described coolant pump.Power-actuated coolant pump according to the present invention can be controlled as: when described control guiding valve, during in described " closing " position, stop the backflow of cooling liquid from described internal-combustion engine along the direction contrary with the throughput direction of described the second coolant pump.

Advantageously, control and " to close " position for described guiding valve is moved to it by the guiding valve by described motor-drive pump, can guarantee any cooling liquid refluxed from described internal-combustion engine (described backflow due to lack pumping action or pumping action lost efficacy cause) along the direction contrary with the throughput direction of described the second coolant pump, mobile towards the radiator of described vehicle.

As for the parallel join of two pumps, it should be noted that parallel flow path also forms bypass flow path.Medium to be conveyed flows along the direction of low pressure all the time.

Because described main refrigerant fluid pump forms an obvious higher transmission pressure at run duration, move to it by the control guiding valve by described the second coolant pump and " close " position, can guarantee that when described main pump is opened the backflow to suction side is prevented from via described the second pump for discharge side from described main pump.

According to an embodiment, described electric coolant pump is designed to radial flow pump, the cooling liquid to be conveyed wherein shifted from the cooling liquid pipeline can be introduced in the pump chamber be formed on pump case by being substantially conical extension entrance, and the described cooling liquid be introduced in pump chamber can be discharged by outlet from described pump chamber, and described outlet is arranged as substantially and radially meets at right angles with entrance pipe.

Described pump impeller is designed to the radial flow pump impeller and is arranged in described pump chamber suck cooling liquid and described cooling liquid radially is transported to outlet port by axial rotatablely moving.Described guiding valve is designed to be arranged on described impeller and the control guiding valve coaxial with described pump shaft; And preferably, described motor is disposed on the part of described pump case away from described entrance; Wherein said motor comprises the live axle extend in described pump chamber, described impeller and described control guiding valve are arranged in coaxially on described live axle and are maintained on described live axle in the mode of Spielpassung, preferably, by holding member, described impeller and described control guiding valve are remained on described live axle, and be designed to columniform control guiding valve seal described impeller and can be along described impeller move axially to " opening " and " closing " position.

According to an embodiment, the mode that described control guiding valve penetrates with the blade by described impeller is connected on described impeller.

Because the assembly be comprised of described impeller and described control guiding valve has compact design, can reduce significantly the requirement to the space of motor.

According to an embodiment, described motor is configured to the dry type rotor and realizes the sealing of described pump chamber by being arranged in shaft seal on live axle.In an alternative embodiment, described motor is configured to the wet type rotor and comes cooling by the cooling liquid of being carried by described coolant pump.

According to an embodiment, be provided at actuator in pump case by least one and the control guiding valve is moved to it " open " and/or " closing " position.Therefore described actuator can be designed to pneumatic, the described guiding valve of driving magnetic force and/or hydraulic pressure, or described actuator can be designed to the electrical servo motor.

In an exemplary embodiment, described actuator can be disposed in the front area of described live axle and is engaged on the part of the front side that is formed on described control guiding valve and has the shape of similar compartment, with relatively described impeller, described control guiding valve is moved to it and " opens " and " closing " position.

Alternately or additionally, described actuator also can be disposed between described impeller and described control guiding valve.For example, described actuator is a rocking arm, described rocking arm is connected to described control guiding valve and described rocking arm by described impeller can be by hydraulically, pneumatically or the stop position (be " open " position of described control guiding valve) of magnetic force ground from it in abutting connection with described impeller move to the position (being " closing " position of described control guiding valve) separated with described impeller.

Described actuator also can be formed in the wall of described pump case, and the groove or the compartment that for this purpose, provide for example are provided.

According to another embodiment, described control guiding valve comprises the part of the compartment shape of sealing described live axle, the part of described compartment shape is towards described entrance and have the helical thread portion be formed on its inner peripheral surface, and the helical thread portion wherein matched with the described helical thread portion of described control guiding valve is formed on the part away from motor of live axle of described electric coolant pump.According to the present invention, intermeshing by described helical thread portion, described control guiding valve is moved along described live axle.

Due to the described helical thread portion matched being provided, advantageously, just, without the other driving mechanism for described control guiding valve is provided in described electric coolant pump, this will allow the spatial requirement reduced described pump further to reduce cost and simplified described pump structure simultaneously.

According to another embodiment, described control guiding valve is designed to along the profile of the front side of described impeller and has the radially continuous closed component that is arranged in described control guiding valve outer end, and the first black box that wherein radially is arranged in the outside of described control guiding valve is configured in the end of described closed component away from described motor.

According to another embodiment of described electric coolant pump, an accommodating part is formed in described pump chamber, and the closing assembly of described control guiding valve described control guiding valve when it " opens " position can be inserted in described accommodation section.

Because not be used in the additional space that the inside of described pump chamber is provided for the closing assembly of described control guiding valve, providing of described accommodation section allows the size of described coolant pump further to reduce in a kind of favourable mode.

According to an embodiment of described coolant pump, radially be arranged in the second black box in described control guiding valve be configured in described impeller on the radial outer end of described motor.According to preferred embodiment, therefore the diameter of described the first black box can be designed to be greater than the diameter of described the second black box.

According to an embodiment, when in " closing " position, the outlet of described motor can be closed via described closed component, described the first black box and described the second black box hermetically by described control guiding valve.

The structure of described control guiding valve makes its profile along the front side of described impeller, the compactness that described structure allows the assembly of described impeller and described control guiding valve to be designed.And described black box is provided on described control guiding valve and described impeller, make when described control guiding valve during in " closing " position described electronic delivery side of pump in a kind of favourable mode by safe sealing, meanwhile, when described control guiding valve during in " closing " position, the closed component of described control guiding valve is supported described impeller in the following manner, described mode is: any back pressure that described cooling liquid produces all can not move or crooked described control guiding valve, and described movement or bending can cause the fluid leakage in described coolant pump.

In another embodiment according to coolant pump of the present invention, brake assemblies further is provided, rely on the described impeller of described brake assemblies can be fixed on the inwall of described pump case.

According to an embodiment, therefore described brake assemblies is formed on described impeller and preferably consists of prestressing force brake spring or dish shape brake disc, described brake assemblies comprises and is positioned at its radially outer end wedge-like thickened section of the taper of direction inwardly radially, preferably, wherein rely on described wedge-like thickened section, thus described brake assemblies can with pump housing endophragm surface friction in abutting connection with described motor engage described impeller be fixed on described pump case.

According to another embodiment, the described brake assemblies of increase that the described brake assemblies that specifically comprises described thickened section is designed to the vane rotary speed that the live axle along with described motor causes breaks away from from the inwall of described pump case, thereby described impeller is broken away from.

By this layout, can described impeller be fixed on the wall of described pump chamber a kind of favourable and easy mode, only have described control guiding valve can be moved to it when described live axle rotation and " open " or " closing " position.

When described control guiding valve arrives at its " opening " position fully, form interference fit between the impeller on described live axle and described control guiding valve, this makes the rotation of described live axle be delivered to described impeller.Along with described drive shaft speed increases, centrifugal force makes described brake assemblies break away from from the wall of described pump case, and described impeller can be rotated.Advantageously, this allows described control guiding valve move reliably and can therefore not rotate described impeller along described live axle.

In addition, advantageously, when described control guiding valve and described impeller engages and described impeller and described control guiding valve between interference fit while making the rotation of described live axle be passed to described impeller, a kind of start-up operation can be by favourable realization.This makes the mild increase of transfer rate of described electric coolant pump.

The present invention proposes a kind of suitable impeller and controls the method according to the stream of the cooling liquid in cooling system of the present invention in addition.

Above-mentioned advantage also can be similar to is applied to according to impeller of the present invention and is applied in the method for the cooling liquid stream of Controlled cooling system.

According to an embodiment, described impeller comprises: several pieces blades, groove, control guiding valve and brake assemblies; Described several pieces blades preferably typical radial flow pump blade and be formed on described impeller on the surface of cooling liquid entrance; Described groove is for holding live axle; Described control guiding valve is connected on described impeller; Described brake assemblies is arranged on described impeller.

Advantageously, impeller according to the present invention is applicable to above-mentioned according to coolant pump of the present invention with comprise in the corresponding cooling system of described coolant pump.

In an embodiment of described impeller, described control guiding valve is included in the first black box that its front end radially is arranged in its outside, and wherein said impeller is included in it and radially radially is arranged in the second black box of described control guiding valve inboard in outer end.

According to another embodiment, described control guiding valve is configured to described impeller as a whole, so that the blade of described impeller can penetrate described control guiding valve vertically.

In another embodiment according to impeller of the present invention, described brake assemblies is formed on the rear side surface of described impeller.

According to embodiments of the invention, described brake assemblies consists of prestressing force brake spring or dish shape brake disc, and the surface friction ground that described brake assemblies can be relative with the back surface with described impeller engages, so that described impeller is fixed to this surface.

According to another embodiment, described brake assemblies is designed to: the braking effect of described brake assemblies is along with the rotational speed of described impeller increases and weakens, thereby described brake assemblies breaks away from described impeller near the back surface of described impeller whereby.

In another embodiment according to impeller of the present invention, described control guiding valve is designed to along the profile of described impeller and is included in the radially continuous closed component of its outer end.

Therefore according to an embodiment, described control guiding valve is included in the part of compartment shape of the hollow of its front area, and the part of described compartment shape has the helical thread portion be formed on its inner peripheral wall.

According to an embodiment, method according to the stream of the cooling liquid in the cooling system of controller motor vehicle of the present invention, wherein said cooling system comprises controllable main refrigerant fluid pump and controllable the second coolant pump, the mechanical driving of driving force that described main refrigerant fluid pump is disposed in the internal-combustion engine in vehicle, the motor that described the second coolant pump is arranged separately drives electrically; Described method comprises step: the current operating conditions of the internal-combustion engine checked vehicles; The coolant temperature of the cooling liquid that detection circulates in the coolant circuit of vehicle; Read the control parameter from cooling circuit figure; Control described main refrigerant fluid pump and described the second coolant pump according to the control parameter read from cooling circuit figure; And control described cooling liquid stream by the described main refrigerant fluid pump of selectable switch and/or the second coolant pump.

A preferred embodiment of the method according to this invention, the current operating conditions of described internal-combustion engine at least comprises that starting-stop operating mode, pre-thermal condition, low year operating mode, standard load operating mode, fuel-economizing operating mode (eco condition), high rotating speed operating mode and waste heat stores operating mode.

Described startup-stop operating mode referring to following power regime: in described startup-stop described internal-combustion engine temporary close under operating mode (for example, when red light time engine shutdown or other similar situation) to save fuel oil.

Described pre-thermal condition refers to following power regime: i.e. under described pre-thermal condition when internal-combustion engine cold start-up (especially), thus the circulation of interrupting described cooling liquid makes described internal-combustion engine can reach fast its best running temperature so that water stagnates in described cooling system.

The described low operating mode of carrying refers to following power regime:, described low carrying under operating mode, described internal-combustion engine moves with the slow-speed of revolution, for example slow-speed of revolution operation under standby mode.

Described standard load operating mode refers to following power regime:, under described standard load operating mode, described internal-combustion engine moves to vehicle, to apply driving force at medium rotating speed preferably.

Described fuel-economizing operating mode refers to following power regime: under described fuel-economizing operating mode, described internal-combustion engine is normal to be moved and by described cooling system being got involved control, described coolant temperature is maintained on the level of a rising, thereby therefore makes the more effective burning of fuel improve oil consumption.

Described high rotating speed operating mode refers to following power regime:, under described high rotating speed operating mode, described internal-combustion engine is with high rotating speed operation and need reinforcement cooling, for example, in running on expressway or other similar situation.

Finally, described waste heat stores operating mode and refers to following power regime: at described waste heat, store under operating mode, described internal-combustion engine is switched off and coolant temperature should be grown as far as possible remains at higher temperature to shorten the described warm-up phase while starting described internal-combustion engine, and this operating mode can make described internal-combustion engine quickly in it in best temperature range.

According to an embodiment, the control parameter in described cooling circuit figure at least comprises required coolant temperature and/or required motor temperature and/or required cooling liquid flow rate and/or similar parameter.

According to one embodiment of the method for the invention, when the current operating conditions of described internal-combustion engine is pre-thermal condition, along with closing of described control guiding valve, described the second coolant pump is switched to the described control guiding valve that " shut " mode" operating mode and the cooling liquid stream by described main refrigerant fluid pump is disposed in described main refrigerant fluid pump and interrupts, and has therefore interrupted the circulation of cooling liquid.

According to one embodiment of the method for the invention; when the current operating conditions of described internal-combustion engine be while starting-stopping operating mode (described startup-stop under operating mode during the engine shutdown stage; described main refrigerant fluid pump temporarily runs out of steam); described the second coolant pump is switched to opens the pattern operating mode, and the described pattern operating mode of opening makes by the second coolant pump described cooling liquid that circulates.

According to one embodiment of the method for the invention, when the current operating conditions of described internal-combustion engine is low year operating mode, cooling liquid stream by described main refrigerant fluid pump is disposed in that control guiding valve in described main refrigerant fluid pump interrupts and described the second coolant pump is switched to and opens the pattern operating mode, rely on the described pattern operating mode of opening, described cooling liquid is by described the second coolant pump circulation.

According to one embodiment of the method for the invention, when the current operating conditions of described internal-combustion engine is the standard load operating mode, described the second coolant pump is switched to the " shut " mode" operating mode and its control guiding valve is moved to described " cutting out " position, rely on this mode, the cooling liquid in described cooling circuit circulates by described main refrigerant fluid pump.

According to one embodiment of the method for the invention, when the current operating conditions of described internal-combustion engine is the fuel-economizing operating mode, rely on the free wheel device on the belt transmission system that is configured in described main refrigerant fluid pump, the operation of described main refrigerant fluid pump is by the interruption of selectivity, or is arranged in described control guiding valve in described main refrigerant fluid pump and is controlled as and interrupts described cooling liquid and flow in described main refrigerant fluid pump and described cooling liquid circulates to obtain the motor temperature of required rising by described the second coolant pump.

According to one embodiment of the method for the invention, when the current operating conditions of described internal-combustion engine is high rotating speed operating mode, the cooling liquid of described main refrigerant fluid pump flow to small part and be driven to the suction side of the described main refrigerant fluid pump that leads to described internal-combustion engine via described the second coolant pump under bypass mode.

According to one embodiment of the method for the invention; when the current operating conditions of described internal-combustion engine is the waste heat storage operating mode of engine shutdown, the control guiding valve of described main refrigerant fluid pump and the control guiding valve of described the second coolant pump all are closed to stop the circulation of the cooling liquid in cooling circuit.

The accompanying drawing explanation

Described feature of the present invention and function and the further aspect of the present invention and feature, be described further the detailed description of the preferred embodiment based on to following and corresponding accompanying drawing before.

Figure 1A illustrates the perspective elevation according to controllable cooling system of the present invention;

Figure 1B illustrates the perspective back view according to controllable cooling system of the present invention;

The partial sectional view that Fig. 2 A is the power-actuated coolant pump in " opening " position according to an embodiment of the invention;

The detailed drawing that Fig. 2 B is A part in Fig. 2 A;

The partial sectional view that Fig. 3 A is the power-actuated coolant pump in " closing " position according to an embodiment of the invention;

The detailed drawing that Fig. 3 B is A part in Fig. 3 A;

The detailed drawing that Fig. 3 C is B part in Fig. 3 A;

Fig. 4 is according to impeller of the present invention, is furnished with the control guiding valve on described impeller;

The partial sectional view that Fig. 5 is Fig. 4, show the cross section through described control guiding valve; And

Fig. 6 is the partial sectional view that has the impeller of layout control guiding valve thereon in Fig. 4.

Embodiment

Figure 1A shows the perspective view of controllable according to the preferred embodiment of the invention cooling system 1.

According to this embodiment's described cooling system 1, by cooling circuit, formed, described cooling circuit is for supply and the discharge of the cooling liquid of the internal-combustion engine (not shown) from/to vehicle, and wherein said cooling liquid is carried out heat exchange via the heat exchanger and the vehicle periphery that are arranged in the cooling liquid pipeline.

As described in Figure 1, cooling line 13 leads to an entrance 17 be formed on main refrigerant fluid pump 3 from described vehicle radiator.In an illustrated embodiment, therefore described entrance 17 is designed to flanged, but also can be designed as pipeline, bell tap, hole, screw thread, bayonet connector or other similar form.

In an illustrated embodiment, described main refrigerant fluid pump 3 is designed to a kind of radial flow pump and comprises the pump case with pump chamber, and described pump chamber is formed in described pump case, and impeller is arranged in described pump chamber.Described impeller is designed to a kind of radial flow pump impeller and is arranged on the pump shaft in the pump case of main refrigerant fluid pump 3.

Use with transmission the driving mechanism as main refrigerant fluid pump 3 in the embodiment who discusses.

As shown in the rear view of the cooling system shown in Figure 1B, via V band or toothed belt (not shown), be connected to belt wheel 57 on the belt wheel of described internal-combustion engine at described main refrigerant fluid pump 3 on the cross section away from described entrance 17.During internal combustion engine operation, the rotatablely moving of belt wheel 57 that is delivered to described main refrigerant fluid pump 3 by belt drives described belt wheel 57.

As mentioned above, the main refrigerant fluid pump 3 described in this embodiment is a kind of coolant pumps of axially supplying with, relies on the impeller in described pump chamber, described main refrigerant fluid pump 3 will cooling liquid to be conveyed radially direction outwardly transfer to and export 15.In an illustrated embodiment, described outlet 15 is designed to the flanged of similar entrance 17.But also be designed to pipeline, bell tap, hole, screw thread, bayonet connector or other similar form in a lot of situations.

The described main refrigerant fluid pump 3 of discussing in this embodiment further is included in the control guiding valve (also not shown) in its pump chamber, described guiding valve is by coaxial being arranged on live axle, seal described impeller and when " closing " position of described guiding valve around the fringe region of described impeller to interrupt flowing of the cooling liquid of being carried by described main refrigerant fluid pump 3.

For example, by the application and the discussion (DE102005004315B4, DE102005062200B3 and WO2009/14382A2) carried out, the successful marketization of such pump.

And for example, shown in Figure 1A, this embodiment's described main refrigerant fluid pump 3 comprises described outlet 15, and described cooling liquid is transported to described internal-combustion engine via described outlet 15 from described main refrigerant fluid pump 3.

In addition, heating circuit also may be provided in this cooling system, and described cooling system can be used for via heating pipe 19, cooling media being incorporated into described heating circuit from described main refrigerant fluid pump 3.Regulator or the valve that for example, may be arranged in described main refrigerant fluid pump 3 guide the coolant flow of being carried by described pump 3 in described heating circuit.

The described cooling liquid spread out of from described vehicle radiator is fed into described main refrigerant fluid pump 3 via cooling line 13.

The second coolant pump 5 is arranged to described main refrigerant fluid pump 3 parallel.Entrance 9 to described the second coolant pump 5 is a bit located in the upstream of the entrance 17 of described main refrigerant fluid pump 3, and from described cooling line, 13 branches draw.

In this embodiment, described the second coolant pump 5 is designed to equally the pump of a kind of axial supply, radial delivery and moves by motor 7, and described motor 7 is arranged in described the second coolant pump 5 on the part away from described cooling liquid entrance 9.

The described cooling liquid transmitted from described feed pipeline 13 is via the described entrance 9 of point gradually coning, by the pumping action that is arranged in the impeller 25 in described the second coolant pump 5, be inhaled in described the second coolant pump 5, and described cooling liquid is carried to the outlet 15 of described main refrigerant fluid pump 3 via the impeller 25 and the outlet 11 that are arranged in pump chamber 53 from the second coolant pump 5, so does not flow through described main pump 3.Therefore described the second coolant pump 5 forms bypass, the cooling liquid to be conveyed of passing described bypass can be used as the bypass cooling liquid and circulates in described cooling circuit, and described bypass cooling liquid is walked around described main refrigerant fluid pump 5 and flow to described internal-combustion engine from described radiator.

Described entrance 9 and the described outlet 11 of the second coolant pump shown in described embodiment are designed to flanged.But they also can be designed as pipeline, bell tap, hole, screw thread, bayonet connector or other similar form.

The partial sectional view of the power-actuated coolant pump 5 shown in Figure 1A and Figure 1B is shown in Fig. 2 A.

As mentioned above, therefore the described coolant pump 5 shown in Fig. 2 A is designed to the pump of a kind of axial supply, Radial Flow, and described coolant pump 5 comprises the pump chamber 53 be formed in pump case 51.

In embodiment as shown in Figure 2 A, motor 7 is disposed in described the second coolant pump 5 towards the end away from described entrance 9.Therefore this embodiment's described motor has at 20W to the power stage between 100W and is designed to the dry type rotor, and it is lower that described motor can reach the high-engine rotating speed and the energy loss that surpass 12000 rev/mins.

From the live axle 21 of described motor 7s, extend into the described pump chamber 51 of described the second coolant pump 5.

In the embodiment who illustrates herein, described live axle 21 seals described cooling liquid to avoid described cooling liquid to enter into described motor 7 by shaft seal 29.

Described impeller 25 and control guiding valve 31 are by coaxial being arranged on described live axle 21.Described impeller 25 is therefore by keeping assembly 47 to be maintained on described live axle in the mode of Spielpassung.

Therefore the shape of described control guiding valve 31 is substantially along the profile of the front area of described impeller 25, and described impeller 25 has the blade 39 that runs through described control guiding valve upside.

Be formed with the part 33 of sleeve-shaped or compartment shape in the front portion of described control guiding valve 31, the part 33 of described sleeve-shaped or compartment shape has the thread section on the circumference that is provided at its inwall.

The thread section matched with above-mentioned thread section is formed on the front portion 23 of described live axle 21.

Fig. 2 A shows the situation that described the second coolant pump 5 is " opening " in described control guiding valve.

In the situation that, shown in Fig. 2 A, therefore the described cooling liquid of carrying by impeller 25 can radially outward deliver from described the second coolant pump.

As shown in the detailed drawing of A part in Fig. 2 A, black box 45 radially is arranged in the outer end of described impeller 25, in the closed component 35 of controlling guiding valve 31.Another black box 43 radially is arranged in the outside front side of described control guiding valve 31.

In addition, hold described closed component 35 and along the circumference profile of described control guiding valve and conglobate groove 37 is disposed in the pump house wall that faces described motor 7.When described control guiding valve 31 during in " opening " position, described impeller 25 is formed on described closed component 35 on described control guiding valve 31 and is accommodated in described accommodation section 37 and by rotatable and remains in described accommodation section 37, so that can rotate by the driving force of described live axle 21 along with the described control guiding valve 31 formed thereon.

Fig. 3 A shows Fig. 2 A of described control guiding valve in " closing " position and controllable power-actuated the second coolant pump 5 of 2B.

As what illustrate in Fig. 2 A and 3A, the described live axle 21 of described motor 7 moves to corresponding working position by rotating slowly forward and backward by the described control guiding valve 31 of described coolant pump 5 respectively.

Specifically, by along the direction forward pumping direction of described coolant pump 5 (along) rotation slowly, described live axle 21 " is closed " position by described control guiding valve 31 from it and is moved to described " opening " position, when described " opening " position, described control guiding valve 31 is along the profile of described impeller 25, in abutting connection with the surface of described impeller 25, so that described impeller blade 39 can penetrate described control guiding valve 31 and produce pumping action in described coolant pump 5 when described impeller rotates with working speed.

Specifically, described control guiding valve 31 1 contacts with described impeller 25, interference fit between described control guiding valve 31 and described impeller 25 just produces at once, and described interference fit allows described impeller 25 to rotate by the driving force that is delivered to described control guiding valve 31 from described live axle 21.When " opening " position shown in Fig. 2 A, therefore the described cooling liquid of being transported by described impeller 25 can be delivered out described coolant pump 5.

On the contrary, when the counterrotating of described live axle moves to " closing " position shown in Fig. 3 A by described control guiding valve 31, the described control guiding valve 31 in its complete " cutting out " position contacts with the wall section of the described entrance 9 of facing of described pump case 51.

Be formed on the wall that therefore described black box on described control guiding valve 31 43 be compressed in described pump case and the described outlet 11 with respect to described pump 5 seals by described pump chamber 53.The described black box 45 of being supported by described closing assembly 35 be formed on the rear portion of described impeller 25 is designed to the described excircle supporting leg of controlling guiding valve 31, therefore to produce sealing effect fully reliably.

As Fig. 2 B and 3B illustrate, the described black box 43 be formed on described control guiding valve 31 is designed to be greater than the black box 45 be formed on described impeller 25, with the sufficient sealing effect of the wall surface of obtaining relatively described pump chamber.Specifically, due to different sealed diameters, the annular region produced to the difference of the diameter by described

black box

43,45 from the back pressure of the discharge side of described main refrigerant fluid pump 3 is exerted pressure.No matter therefore whether the motor 7 of described the second coolant pump 5 turns round, the sealing function of described

black box

43,45 is all hydraulically strengthened.

For fear of the rotation of the described impeller caused due to carelessness, brake assemblies 27 is disposed in described impeller 25 on the end away from described entrance 9, and described brake assemblies 27 is pressed on the inner wall surface 49 of contiguous described motor 7 in described pump case 51.

Therefore described brake assemblies 27 is designed to brake disc or prestressing force belleville spring, and the wedge-like thickened section 41 that has in an illustrated embodiment the taper of the radial outer end that is positioned at described brake assemblies 27, described wedge-like thickened section 41 frictionally engages the inner wall surface 49 of described pump case 51.

Once thereby moving to it with speed rotation slowly by described control guiding valve 31, the described live axle 21 of described motor 7 " opens " position, described brake assemblies 27 just makes described impeller 25 remain under the state of the joint rubbed with described pump case 51 at once, therefore prevents the excessive rotation of described impeller 25.

When the rotation that between described control guiding valve 31 and described impeller 25 is interference fit and described live axle 21 speeds gradually, the cumulative centrifugal force produced by the rotation of described live axle 21 makes described brake assemblies 27 separate from the wall 49 of described pump case 51, and described impeller 25 can be rotated and therefore produce the pumping action of described coolant pump 5.

The perspective view of the impeller 25 that Fig. 4 is the controlled electric coolant pump 5 with control guiding valve disposed thereon shown in Fig. 3 and Fig. 2.

As shown in this front elevation, along with described impeller blade 39 penetrates described control guiding valve 31, described control guiding valve 31 seals described impeller 25(fully and is not shown specifically).

Described control guiding valve 31 is included in the part 33 of the compartment shape of the center, and the part 33 of described compartment shape is for holding the described live axle 21 of described motor 7.As shown in Figure 5, the part 33 of described compartment shape has thread section on wall within it, and thread section 23(Fig. 5 of described thread section and described live axle 21 is not shown) match.

Fig. 5 be one axially supply with, the partial sectional view of the impeller 25 of radial delivery, during described impeller is used to be designed to the described pump 3,5 of radial flow pump in present discussed embodiment.

If described coolant pump 3,5 is designed to axial-flow pump, so described impeller 25 also can be used for supply radially and carries vertically described cooling liquid.

At described impeller 25 center, the accommodating part 55 of bush type is formed for holding described live axle 21(not shown).

The whole-cutaway view that Fig. 6 is the described impeller 25 with control guiding valve 31 disposed thereon in Fig. 5.As shown in FIG., described impeller 25 and described control guiding valve 31 to be arranged to mutually and coaxially and along the live axle 21 extended to from described motor 7 described pump chamber 51 to extend (in order showing more clearly, described live axle 21 is not shown in Figure 6).

Live axle 21 by described motor 7 correspondingly rotates forward and backward respectively, and described control guiding valve 31 can be moved to required " opening " or " cutting out " position.

With mechanically operated controllable coolant pump 3 and power-actuated controllable coolant pump 5 can estimate to arrange different operating conditionss by the control parameter to default in a kind of favourable mode according to cooling system of the present invention, described control parameter example is coolant temperature and/or required motor temperature and/or required cooling liquid flow rate and/or other similar parameter as required.

Therefore, in order to control described cooling system 1, the additional control gear be configured in the embodiment who discusses according to the present invention is controlled described mechanically operated main refrigerant fluid pump 3 and described power-actuated the second coolant pump 5, so that it reaches operating conditions separately.

Therefore exemplary operating conditions comprises that starting-stop operating mode, pre-thermal condition, low year operating mode, standard load operating mode, fuel-economizing operating mode, high rotating speed operating mode and waste heat stores operating mode.

For example, if cooling system discussed herein 1 is used in and comprises and start-stop in the vehicle of controlling and internal-combustion engine is shut down (when red light); from engine shutdown, cause after described mechanically operated coolant pump 3 do not rerun, described electric coolant pump 5 can lean on the described cooling liquid that himself circulates.

For this purpose; according to currently discussed embodiment; when the current operating conditions of described internal-combustion engine is (in described startup-stop under operating mode while starting-stopping operating mode; described main refrigerant fluid pump 3 temporarily runs out of steam during the engine shutdown stage); described the second coolant pump 5 is switched to opens the pattern operating mode, and the described pattern operating mode of opening makes by the second coolant pump 5 described cooling liquid that circulates.

In addition, described pre-thermal condition refers to following power regime: i.e. under described pre-thermal condition when internal-combustion engine cold start-up (especially), thus the circulation of interrupting described cooling liquid makes described internal-combustion engine can reach fast its best running temperature so that water stagnates in described cooling system 1.

When the current operating conditions of described internal-combustion engine is pre-thermal condition, described the second coolant pump 5 is switched to the described control guiding valve that " shut " mode" operating mode and the cooling liquid stream by described main refrigerant fluid pump 3 is disposed in described main refrigerant fluid pump and interrupts, and has therefore interrupted the circulation of cooling liquid.

Therefore can control the pump 3,5 under the internal-combustion engine warm-up phase in following mode with the cooling system 1 in currently discussed embodiment: the guiding valve of described pump 3,5 all is closed and cooling liquid can not be by two described pumps 3,5 circulations.Equally therefore described electric drive coolant pump 5 cuts out, and stops backflow and liquid circulation by closing described control guiding valve 31 thereupon.Alternately, described pump 5 is controlled as and makes described control guiding valve 31 stop liquid circulation.

In this manner, likely reach fast the running temperature of described internal-combustion engine.

In addition, the described low operating mode of carrying refers to following power regime:, described low carrying under operating mode, described internal-combustion engine moves with the slow-speed of revolution, for example slow-speed of revolution operation under standby mode.

According to currently discussed embodiment, when the current operating conditions of described internal-combustion engine is low year operating mode, cooling liquid stream by described main refrigerant fluid pump 3 is disposed in that control guiding valve in described main refrigerant fluid pump interrupts and described the second coolant pump 5 is switched to and opens the pattern operating mode, rely on the described pattern operating mode of opening, described cooling liquid is by described the second coolant pump 5 circulations.

Also likely, when described internal-combustion engine moves with low-down rotating speed, because this may make the cycle performance deficiency of described main refrigerant fluid pump 3, so additionally the second coolant pump 5 of described electric power is opened (this electric power boosting that is otherwise known as), then auxiliary liquid circulation of the i.e. pump displacement based on described controllable the second electric coolant pump 5 of speech.

Under the high capacity operating mode of described internal-combustion engine (such as driving on expressway etc.), the control guiding valve 31 of described power-actuated coolant pump 3 usually is moved to it and " cuts out " position or described pump 3 is closed and the circulation of described cooling liquid only realizes via described mechanically operated main refrigerant fluid pump 3.

If but needing additional cooling capacity, described electrical coolant pump 5 can additionally be opened to assist described mechanical coolant pump 3 to carry described cooling liquid.

Described standard load operating mode refers to following power regime:, under described standard load operating mode, described internal-combustion engine moves to vehicle, to apply driving force at medium rotating speed preferably.At this moment, described the second coolant pump 5 is switched to the " shut " mode" operating mode and its control guiding valve 31 is moved to described " cutting out " position usually, relies on this mode, and the cooling liquid in described cooling circuit circulates by described main refrigerant fluid pump 3.

When described internal combustion engine operation under gas-saving mode (fuel-economizing operating mode), rely on the free wheel device on the belt wheel 57 that is configured in described main refrigerant fluid pump 3, the operation of described main refrigerant fluid pump is by the interruption of selectivity, and/or is arranged in described control guiding valve in described main refrigerant fluid pump 3 and is controlled as and interrupts described cooling liquid and flow in described main refrigerant fluid pump 3.Under such operating mode, described cooling liquid circulates to obtain the motor temperature of required rising by described the second coolant pump 5.

Embodiment according to the method according to this invention, when the current operating conditions of described internal-combustion engine is high rotating speed operating mode, the cooling liquid of described main refrigerant fluid pump 3 flow to small part and be output to the suction side of the described main refrigerant fluid pump 5 that leads to described internal-combustion engine via described the second coolant pump 5 under bypass mode.

Finally, described waste heat stores operating mode and refers to following power regime: at described waste heat, store under operating mode, described internal-combustion engine is switched off and coolant temperature should be grown as far as possible remains at higher temperature to shorten the described warm-up phase while starting described internal-combustion engine, rely on the described internal-combustion engine of this operating mode can be quickly in it best temperature range.

In the currently discussed embodiment of cooling system 1, rely on and be arranged in described pump 3, guiding valve on 5 is turned off two described pumps 3,5, and then stoping the backflow of cooling liquid from motor to described radiator, this makes heat exchange between described cooling liquid and vehicle-periphery can be only occur in the mode of very big time delay.Therefore when described vehicle during in vehicle stop state, the heat that described internal-combustion engine produces can be preserved very long a period of time, and described heat can be in use during restarting subsequently to reach described optimum temperature faster.

Embodiment discussed herein relates to a kind of power-actuated the second coolant pump 5, although the control guiding valve 31 in described the second coolant pump 5 relies on the driving mechanism that is designed to threaded mandrel to move along described live axle 21, described control guiding valve 31 also can rely on pneumatic, magnetic force and/or hydraulically powered actuator or electrical servo motor and not move with respect to described impeller along described live axle 21 by described threaded mandrel.

Although embodiment discussed herein discloses a kind of control guiding valve 31 be formed in discretely on impeller 25, described control guiding valve 31 also can be integrally formed in described impeller 25.For example, the control guiding valve 31 be integrally formed in described impeller 25 can be designed to make the closed component 35 of leg shape wall zone and described control guiding valve 31 to have identical effect, and described closed component 35 is formed on the outer surface of described impeller 25.

In order to control the cooling liquid stream of being carried by the second coolant pump 5 of outfit like this, impeller 25 is designed to move along described live axle 21, thereby so that described leg shape wall assembly stretches out and closes hermetically described outlet 11 towards the rear side of described pump case when the described impeller 25 of so design is in the closed position.In " opening " position with controlling the integrally formed described impeller 25 of guiding valve 31, described wall assembly is arranged in described accommodation section 37 so that they can be around described live axle 21 rotations, and described accommodation section 37 is formed in the wall of described pump case 51.

Alternately, be arranged in the revolving valve that the control guiding valve 31 of described impeller 25 upstreams also can be disposed in described pump chamber 53 and substitute, to seal described impeller 25 and described revolving valve, can be rotated to " opening " position and " closing " position.Also can use the sleeve-shaped that is arranged in described impeller 25 downstreams to control guiding valve, by the example driving of threaded mandrel or pneumatic, magnetic force and/or hydraulically powered actuator or electrical servo motor as previously discussed, described sleeve-shaped is controlled guiding valve and described impeller 25 is pushed and therefore close hermetically subsequently to described the second delivery side of pump 11 on one side.

The impeller of before discussing (controlling guiding valve is arranged on described impeller) also can be used as a kind of one-way valve in pipe-line system.Rely on the direction and the suction pressure that flow into, therefore described guiding valve can further be carried the inflow medium on the axle that keeps described impeller and described guiding valve; Or when and the flowing pressure of throughput direction contrary when very high, " close " position and close described pipe-line system by described control guiding valve being moved to it.

Although electric coolant pump discussed herein 5 comprises motor 7(, described motor 7 has the output power of 20W to 100W), also can use more powerful motor (for example thering is the motor up to the output power of 2KW) so that described electric coolant pump can be used as the circulation (if necessary) that pump unique in described cooling circuit is responsible for cooling liquid.

The present invention relates to a kind of controllable cooling system 1 for vehicle, a kind of mechanically operated controllable main refrigerant fluid pump 3 and a kind of power-actuated controllable the second coolant pump 5, the described cooling circuit that comprises of described controllable cooling system 1, described cooling circuit outputs to internal-combustion engine by cooling liquid and cooling liquid is sent from described internal-combustion engine;

Described cooling system further comprises control gear, and described control gear is controlled described main refrigerant fluid pump 3 and the second coolant pump 5 according to the operating conditions of described internal-combustion engine.The invention provides in addition power-actuated controllable the second coolant pump 5 for described cooling system 1, the method that is used in the impeller 25 of this second coolant pump 5 and controls the cooling liquid stream in described cooling system 1.

Claims

1. the controllable cooling system for motor vehicle (1) comprising:

Cooling circuit, described cooling circuit is for being supplied to cooling liquid the internal-combustion engine of described vehicle and cooling liquid is discharged from the internal-combustion engine of described vehicle;

Mechanically operated controllable main refrigerant fluid pump (3), comprise entrance (17) and outlet (15), and described entrance (17) is for being supplied to cooling liquid described main refrigerant fluid pump (3), and described outlet (15) is for being discharged to cooling liquid in described internal-combustion engine; And

Power-actuated controllable the second coolant pump (5), comprise entrance (9) and outlet (11), described entrance (9) is for being supplied to cooling liquid described the second coolant pump (5), described outlet (11) is discharged towards described main refrigerant fluid pump (3) for the cooling liquid that will carry as bypass cooling liquid stream, wherein:

Described the second coolant pump (5) is disposed in the upstream end of the streamwise of described main refrigerant fluid pump (3), along the direction of coolant flow from cooling line (13) branch of leading to described main refrigerant fluid (3), draws,

Utilize the cooling liquid that described the second coolant pump (5) is carried to be fed into the outlet (15) of leading to described internal-combustion engine with the downstream through described main refrigerant fluid pump (3) and the mode of the described main refrigerant fluid pump (3) of not flowing through,

Described the second coolant pump (5) comprises pump case (51), be formed with pump chamber (53) in described pump case (51), wherein motor (7) is disposed on the part of described pump case (51), described motor (7) relies on the live axle (21) extended in described pump chamber (53) to provide driving force for described the second coolant pump (5)

Described the second coolant pump (5) in described pump chamber (53) comprises impeller (25), described impeller (25) serves as the conveyer assembly, described impeller (25) is arranged to described live axle (21) is coaxially also drivable and is connected to described live axle (21) above, and

Described the second coolant pump (5) comprises the control guiding valve (31) be formed on described impeller (25), described control guiding valve (31) at least can be moved to " opening " position and " cutting out " position, with for controlling the bypass cooling liquid stream of being carried by described the second coolant pump (5), be particularly useful for stoping the direction that cooling liquid is contrary along the throughput direction with described the second coolant pump (5) to reflux.

2. system according to claim 1, wherein, described main refrigerant fluid pump (3) comprises pump case, be formed with pump chamber in described pump case, the impeller that wherein serves as the conveyer assembly is arranged in described pump chamber and, via the drive shaft extended in described pump chamber, described live axle is preferably driven by the band transmission.

3. system according to claim 1 and 2, described main refrigerant fluid pump (3) further comprises the control guiding valve, described control guiding valve is formed on described impeller and with described impeller and arranges coaxially, described control guiding valve at least can be moved to " opening " position and " cutting out " position, to control the cooling liquid stream of being carried by described main refrigerant fluid pump (3), described control guiding valve preferably is arranged in described pump chamber along described impeller.

4. system according to claim 1, wherein, the motor (7) of described the second coolant pump (5) is configured to dry type rotor or wet type rotor.

5. according to the described system of any one in claim 1-4, further comprise control gear, described control gear is controlled described the first main refrigerant fluid pump (3) and/or described the second coolant pump (5) according to the operating conditions distributed of described internal-combustion engine.

6. an electric coolant pump (5), described electric coolant pump (5) is particularly useful for according to the described cooling system of any one (1) in claim 1-5, and wherein said electric coolant pump (5) is designed to axial-flow pump or radial flow pump and comprises:

Pump case (51);

Be preferably flanged entrance (9) and be preferably flanged outlet (11);

Be formed on the pump chamber (53) in described pump case (51); The pump shaft (21) that wherein pump impeller (25) is disposed in described pump chamber (53) is upper, and described pump impeller (25) can be driven by motor (7) by the relaying of described pump shaft (21), and

Guiding valve (31), described guiding valve (31) at least can be moved to " opening " and " cutting out " position to control the bypass cooling liquid stream of being carried by coolant pump (5), is particularly useful for stoping the direction that cooling liquid is contrary along the throughput direction with described the second coolant pump (5) to reflux.

7. electric coolant pump according to claim 6 (5), wherein, described electric coolant pump (5) is designed to radial flow pump and wherein,

The cooling liquid to be conveyed shifted from cooling liquid pipeline (13) can by being substantially conical extension entrance (9), to be introduced in the pump chamber (53) be formed on pump case (51) inner, and describedly be introduced in cooling liquid in pump chamber (53) and can discharge from described pump chamber (53) by outlet (11), described outlet (11) is arranged to substantially radially and entrance pipe (9) meets at right angles; Wherein,

Described pump impeller (25) is disposed in described pump chamber (53) and is designed to as the radial flow pump impeller, and described pump impeller (25) sucks cooling liquid and cooling liquid radially is transported to outlet (11) by axial rotatablely moving;

Described guiding valve (31) is designed to be arranged in described impeller (25) above and the control guiding valve (31) coaxial with described pump shaft (21); And

Described motor (7) preferably is arranged on the part of described pump case (51) away from described entrance (9); Wherein,

Described motor (7) comprises the live axle (21) extend in described pump chamber (53),

It is upper and be maintained on described live axle (21) in the mode of Spielpassung that described impeller (25) and described control guiding valve (31) are arranged in described live axle (21) coaxially, preferably, by holding member (47), described impeller (25) and described control guiding valve (31) are remained on to described live axle (21) above, and

Be designed to columniform control guiding valve (31) seal described impeller (25) and can be along described impeller (25) axially be moved to " opening " and " closing " position.

8. according to the described electric coolant pump of claim 6 or 7 (5), wherein, the mode that described control guiding valve (31) penetrates with the blade by described impeller (25) (39) is connected on described impeller (25).

9. according to the described electric coolant pump of any one (5) in claim 6-8, wherein, described motor (7) is designed to the dry type rotor and realizes the sealing of described pump chamber (53) by the shaft seal (29) be arranged on live axle (21).

10. according to the described electric coolant pump of any one (5) in claim 6-8, wherein, described motor (7) is designed to the wet type rotor and comes cooling by the cooling liquid of being carried by coolant pump (5).

11. according to the described electric coolant pump of any one (5) in claim 6-10, wherein, be disposed in the actuator in coolant pump (5) by least one, described control guiding valve (31) can be mobile along described live axle (21), and wherein: described actuator is designed to the guiding valve of the driving of pneumatic, magnetic force and/or hydraulic pressure; Perhaps described actuator is designed to the electrical servo motor.

12. according to the described electric coolant pump of any one (5) in claim 6-10, wherein, described control guiding valve (31) comprises sealing described live axle (21) and, towards the part (33) of described entrance (9), described part (33) has the helical thread portion be formed on its inner peripheral surface.

13. according to the described electric coolant pump of any one (5) in claim 6-12, wherein, the helical thread portion matched with the described helical thread portion (33) of described control guiding valve (31) is formed on the part away from motor (7) (23) of described live axle (21); , intermeshing by described helical thread portion (23,33), described control guiding valve (31) can be by mobile along described live axle (21).

14. according to the described electric coolant pump of any one (5) in claim 6-13, wherein, described control guiding valve is designed to along the profile of the front side of described impeller (25) and has the radially continuous closed component (35) that is arranged in described control guiding valve outer end, and the first black box (43) that wherein radially is arranged in the outside of described control guiding valve (31) is configured in the end of described closed component (35) away from described motor (7).

15. electric coolant pump according to claim 14 (5), wherein, accommodating part (37) are formed in described pump chamber (53); When described control guiding valve (31), when it " opens " position, the closing assembly (35) of described control guiding valve (31) can be inserted in described accommodation section (37).

16. according to the described electric coolant pump of any one (5) in claim 6-15, wherein, radially be arranged in the second black box (45) in described control guiding valve (31) be configured in described impeller (25) on the radial outer end of described motor (7).

17., according to the described electric coolant pump of any one (5) in claim 14-16, wherein, the diameter of described the first black box (43) is greater than the diameter of described the second black box (45).

18. according to the described electric coolant pump of any one (5) in claim 14-17, wherein, described outlet (11) can be closed via described closed component (35), described the first black box (43) and described the second black box (45) hermetically by the described control guiding valve (21) in " closing " position.

19. according to the described electric coolant pump of any one (5) in claim 6-18, wherein, further provide brake assemblies (27), relied on the described impeller of described brake assemblies (27) (25) can be fixed on the inwall (49) of described pump case (51).

20. electric coolant pump according to claim 19 (5), wherein, described brake assemblies (27) is formed on described impeller (25) above and preferably consists of prestressing force brake spring or dish shape brake disc; Described brake assemblies (27) preferably includes and is positioned at the radially wedge-like thickened section (41) of the taper substantially of direction inwardly of its outer end radially; Wherein preferably rely on described wedge-like thickened section (41), described brake assemblies (27) can be with the inwall (49) in abutting connection with described motor (7) of described pump case (51) thereby is frictionally engaged described impeller (25) is fixed on described pump case (51).

21. according to the described electric coolant pump of claim 19 or 20 (5), wherein, the described brake assemblies (27) that specifically comprises described thickened section (41) is designed to the increase of the rotational speed of the described impeller (25) that the live axle (25) along with described motor (7) causes, described brake assemblies (27) breaks away from from the inwall (49) of described pump case (51), thereby described impeller (25) is broken away from.

22. an impeller (25), described impeller (25) is concrete to be used according to the described coolant pump of any one (5) in claim 6-21 with according in the described cooling system of any one (1) in claim 1-5, and described impeller (25) comprising:

Several pieces blades (39), described several pieces blades (39) preferably typical radial flow pump blade and be formed on described impeller on the surface of cooling liquid entrance (9);

Groove (55), described groove (55) is for holding live axle (21);

Control guiding valve (31), described control guiding valve (31) is connected on described impeller (25);

Brake assemblies (27), described brake assemblies (27) is arranged on described impeller (25).

23. impeller according to claim 22 (25), wherein, described control guiding valve (31) is included in the first black box (43) that its front end radially is arranged in its outside, and wherein said impeller (25) is included in it and radially radially is arranged in inboard the second black box (45) of described control guiding valve (31) in outer end.

24., according to the described impeller of claim 22 or 23 (25), wherein, described control guiding valve (31) and described impeller (25) unitary moulding, so that the blade (39) of described impeller (25) can penetrate described control guiding valve (31) vertically.

25. impeller according to claim 22 (25), wherein, described brake assemblies (27) is formed on the rear side surface of described impeller (25).

26. according to the described impeller of claim 22 or 25 (25), wherein, described brake assemblies (27) consists of prestressing force brake spring or dish shape brake disc, described brake assemblies (27) can be relative with the back surface with described impeller (25) surface friction ground engage, so that described impeller (25) is fixed to this surface.

27. according to claim 22,25 or 26 described impellers (25), wherein, described brake assemblies (27) is designed to: the braking effect of described brake assemblies (27) is along with the rotational speed of described impeller (25) increases and weakens, described brake assemblies (27) is the back surface of close described impeller (25) whereby, thereby described impeller (25) is broken away from.

28., according to the described impeller of any one (25) in claim 22-24, wherein, described control guiding valve (31) is designed to along the profile of described impeller (25) and is included in the radially continuous closed component (35) of its outer end.

29. according to the described impeller of any one (25) in claim 22-24 and 28, wherein, described control guiding valve (31) is included in the part (33) of compartment shape of the hollow of its front area, and the part of described compartment shape (33) has the helical thread portion be formed on its inner peripheral wall.

30. the method for the stream of the cooling liquid in the cooling system of a controller motor vehicle (1), described cooling system (1) is preferably the described cooling system according to claim 1-5, wherein said cooling system (1) comprises controllable main refrigerant fluid pump (3) and controllable the second coolant pump (5), the driving force that described main refrigerant fluid pump (3) is disposed in the internal-combustion engine in vehicle mechanically drives, and the motor that described the second coolant pump (5) is arranged separately drives electrically; Described method comprises step:

The current operating conditions of the internal-combustion engine checked vehicles;

The coolant temperature of the cooling liquid that detection circulates in the coolant circuit of vehicle;

Read the control parameter from cooling circuit figure;

Control described main refrigerant fluid pump (3) and described the second coolant pump (5) according to the control parameter read from described cooling circuit figure; And

Control cooling liquid stream by the described main refrigerant fluid pump of selectable switch (3) and/or described the second coolant pump (5).

31. method according to claim 30, wherein, the current operating conditions of described internal-combustion engine at least comprises that starting-stop operating mode, pre-thermal condition, low year operating mode, standard load operating mode, fuel-economizing operating mode, high rotating speed operating mode and waste heat stores operating mode.

32., according to the described method of claim 30 or 31, wherein, the control parameter in described cooling circuit figure at least comprises required coolant temperature and/or required motor temperature and/or required cooling liquid flow rate and/or similar parameter.

33. method according to claim 31, wherein, when the current operating conditions of described internal-combustion engine is pre-thermal condition, described the second coolant pump (5) is switched to the control guiding valve (31) that " shut " mode" operating mode and the cooling liquid stream by described main refrigerant fluid pump (3) is disposed in described main refrigerant fluid pump (3) and interrupts, and therefore interrupts the circulation of cooling liquid.

34. method according to claim 31; wherein; when the current operating conditions of described internal-combustion engine is while starting-stopping operating mode; during described startup-stop the engine shutdown stage under operating mode; described main refrigerant fluid pump (3) temporarily runs out of steam; described the second coolant pump is switched to and opens the pattern operating mode by (5), and the described pattern operating mode of opening makes cooling liquid pass through described the second coolant pump (5) to circulate.

35. method according to claim 31, wherein, when the current operating conditions of described internal-combustion engine is low while carrying operating mode, the cooling liquid stream by described main refrigerant fluid pump (3) is disposed in that control guiding valve in described main refrigerant fluid pump (3) interrupts and described the second coolant pump (5) is switched to and opens the pattern operating mode; Rely on the described pattern operating mode of opening, cooling liquid circulates by described the second coolant pump (5).

36. method according to claim 31, wherein, when the current operating conditions of described internal-combustion engine is the standard load operating mode, described the second coolant pump (5) is switched to the " shut " mode" operating mode and its control guiding valve (31) is closed, rely on this mode, the cooling liquid in described cooling circuit circulates by described main refrigerant fluid pump (3).

37. method according to claim 31, wherein, when the current operating conditions of described internal-combustion engine is the fuel-economizing operating mode,

Rely on the free wheel device on the belt transmission system be configured in described main refrigerant fluid pump (3), the operation of described main refrigerant fluid pump (3) is by the interruption of selectivity, or

The described control guiding valve be arranged in described main refrigerant fluid pump (3) is controlled as: the interruption cooling liquid flow in described main refrigerant fluid pump (3) and cooling liquid circulates by described the second coolant pump (5), to obtain the motor temperature of required rising.

38. method according to claim 31, wherein, when the current operating conditions of described internal-combustion engine is high rotating speed operating mode, the cooling liquid of described main refrigerant fluid pump (3) flow to small part and be driven to the suction side of the described main refrigerant fluid pump (5) that leads to described internal-combustion engine via described the second coolant pump (5) under bypass mode.

39. method according to claim 31; wherein; when the current operating conditions of described internal-combustion engine is the waste heat storage operating mode of engine shutdown; the control guiding valve (31) of the control guiding valve of described main refrigerant fluid pump (3) and described the second coolant pump (5) all is closed, to stop the circulation of cooling liquid in cooling circuit.